US10488124B2 - Corrugated fin heat exchanger, refrigeration cycle apparatus, apparatus for producing corrugated fin, and method for producing corrugated fin heat exchanger - Google Patents
Corrugated fin heat exchanger, refrigeration cycle apparatus, apparatus for producing corrugated fin, and method for producing corrugated fin heat exchanger Download PDFInfo
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- US10488124B2 US10488124B2 US15/558,582 US201515558582A US10488124B2 US 10488124 B2 US10488124 B2 US 10488124B2 US 201515558582 A US201515558582 A US 201515558582A US 10488124 B2 US10488124 B2 US 10488124B2
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- corrugated fin
- flat tube
- angle
- heat exchanger
- slant
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F17/00—Removing ice or water from heat-exchange apparatus
- F28F17/005—Means for draining condensates from heat exchangers, e.g. from evaporators
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D13/00—Corrugating sheet metal, rods or profiles; Bending sheet metal, rods or profiles into wave form
- B21D13/04—Corrugating sheet metal, rods or profiles; Bending sheet metal, rods or profiles into wave form by rolling
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D53/00—Making other particular articles
- B21D53/02—Making other particular articles heat exchangers or parts thereof, e.g. radiators, condensers fins, headers
- B21D53/022—Making the fins
-
- B—PERFORMING OPERATIONS; TRANSPORTING
- B21—MECHANICAL METAL-WORKING WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D—WORKING OR PROCESSING OF SHEET METAL OR METAL TUBES, RODS OR PROFILES WITHOUT ESSENTIALLY REMOVING MATERIAL; PUNCHING METAL
- B21D53/00—Making other particular articles
- B21D53/02—Making other particular articles heat exchangers or parts thereof, e.g. radiators, condensers fins, headers
- B21D53/08—Making other particular articles heat exchangers or parts thereof, e.g. radiators, condensers fins, headers of both metal tubes and sheet metal
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
- F25B39/02—Evaporators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D1/00—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators
- F28D1/02—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid
- F28D1/04—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits
- F28D1/053—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight
- F28D1/0535—Heat-exchange apparatus having stationary conduit assemblies for one heat-exchange medium only, the media being in contact with different sides of the conduit wall, in which the other heat-exchange medium is a large body of fluid, e.g. domestic or motor car radiators with heat-exchange conduits immersed in the body of fluid with tubular conduits the conduits being straight the conduits having a non-circular cross-section
- F28D1/05366—Assemblies of conduits connected to common headers, e.g. core type radiators
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/126—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element consisting of zig-zag shaped fins
- F28F1/128—Fins with openings, e.g. louvered fins
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F19/00—Preventing the formation of deposits or corrosion, e.g. by using filters or scrapers
- F28F19/006—Preventing deposits of ice
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B13/00—Compression machines, plants or systems, with reversible cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B2500/00—Problems to be solved
- F25B2500/01—Geometry problems, e.g. for reducing size
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B39/00—Evaporators; Condensers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
- F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
- F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
- F25B47/02—Defrosting cycles
- F25B47/022—Defrosting cycles hot gas defrosting
- F25B47/025—Defrosting cycles hot gas defrosting by reversing the cycle
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2215/00—Fins
- F28F2215/04—Assemblies of fins having different features, e.g. with different fin densities
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F2265/00—Safety or protection arrangements; Arrangements for preventing malfunction
- F28F2265/14—Safety or protection arrangements; Arrangements for preventing malfunction for preventing damage by freezing, e.g. for accommodating volume expansion
Definitions
- the present invention relates to a corrugated fin heat exchanger, a refrigeration cycle apparatus, an apparatus for producing a corrugated fin, and a method for producing the corrugated fin heat exchanger.
- Patent Literature 1 discloses a heat exchanger in which flat tubes and corrugated fins are alternately stacked in parallel in a lateral direction.
- Each corrugated fin of the heat exchanger includes an upper fin portion having a large angle of inclination and a lower fin portion having a small angle of inclination.
- Patent Literature 1 Japanese Unexamined Patent Application Publication No. 2002-90083
- the present invention has been made in order to overcome the above-described problem, and an object of the present invention is to provide a corrugated fin heat exchanger that is able to prevent the heat exchanger from being broken, a refrigeration cycle apparatus, a method for producing a corrugated fin, and a method for producing the corrugated fin heat exchanger.
- a corrugated fin heat exchanger includes: a first flat tube; a second flat tube aligned in parallel with the first flat tube; and a corrugated fin disposed between the first flat tube and the second flat tube; the corrugated fin including a first slant portion bridging between the first flat tube and the second flat tube and inclined relative to a perpendicular line toward the first flat tube at a first angle of inclination, a second slant portion bridging between the first flat tube and the second flat tube and inclined relative to the perpendicular line at a second angle of inclination, and a third slant portion bridging between the first flat tube and the second flat tube, the third slant portion positioned between the first slant portion and the second slant portion, and inclined relative to the perpendicular line at an angle of inclination larger than both of the first angle of inclination and the second angle of inclination.
- a refrigeration cycle apparatus includes the corrugated fin heat exchanger.
- a production apparatus for a corrugated fin includes: a supply unit configured to supply a band-shaped thin plate; a shaping unit configured to shape the thin plate supplied from the supply unit, into a corrugated shape; and a cutting unit configured to cut the thin plate shaped by the shaping unit, to produce the corrugated fin; the shaping unit including a pair of shaping rollers meshing with each other with the thin plate intervening therebetween; and a plurality of teeth having shapes different from each other are formed on an outer peripheral surface of each of the pair of shaping rollers.
- a method for producing a corrugated fin heat exchanger is a method for producing the corrugated fin heat exchanger, the method including a step of producing the corrugated fin by using the production apparatus for the corrugated fin.
- FIG. 1 is a refrigerant circuit diagram showing a schematic configuration of a refrigeration cycle apparatus according to Embodiment 1 of the present invention.
- FIG. 2 is a perspective view showing the configuration of a corrugated fin heat exchanger according to Embodiment 1 of the present invention.
- FIG. 3 is a front view showing the configuration of a corrugated fin 30 in the corrugated fin heat exchanger according to Embodiment 1 of the present invention.
- FIG. 4 is a schematic diagram showing a production process for the corrugated fin 30 as a part of a production process for the corrugated fin heat exchanger according to Embodiment 1 of the present invention, and a production apparatus used in the process.
- FIG. 5 is a diagram showing a schematic configuration in which the outer peripheral surface of each of shaping rollers 61 and 62 is developed along a supply direction of a thin plate 51 in the production apparatus for the corrugated fin heat exchanger according to Embodiment 1 of the present invention.
- FIG. 6 is a front view showing the configuration of a part of a corrugated fin heat exchanger used in an actual machine test for Embodiment 1 of the present invention.
- FIG. 7 is a diagram showing results of the actual machine test for Embodiment 1 of the present invention.
- FIG. 8 is a diagram showing (a) a state before defrosting of a corrugated fin heat exchanger having a fin pitch Fp of 1.6 mm and (b) a state in the latter half of defrosting thereof, in the actual machine test for Embodiment 1 of the present invention.
- FIG. 9 is a diagram showing (a) a state before defrosting of a corrugated fin heat exchanger having a fin pitch Fp of 1.8 mm and (b) a state in the latter half of defrosting thereof, in the actual machine test for Embodiment 1 of the present invention.
- FIG. 10 is a boundary diagram showing a boundary between presence and absence of sliding-down of frost 35 in the corrugated fin heat exchanger according to Embodiment 1 of the present invention.
- FIG. 11 is an explanatory diagram showing an example of behavior of frost 35 during defrosting in the corrugated fin heat exchanger according to Embodiment 1 of the present invention, and a diagram showing (a) a state in the first half of defrosting and (b) a state in the latter half of defrosting thereof.
- FIG. 12 is a front view showing the configuration of a corrugated fin 30 in a corrugated fin heat exchanger according to Embodiment 2 of the present invention.
- FIG. 13 is an explanatory diagram showing an example of behavior of water of melted frost during defrosting in the corrugated fin heat exchanger according to Embodiment 2 of the present invention.
- FIG. 14 is a perspective view showing the configuration of a corrugated fin 30 in a corrugated fin heat exchanger according to Embodiment 3 of the present invention.
- FIG. 15 is a diagram showing a front view (a) and a side view (b) of the corrugated fin 30 in the corrugated fin heat exchanger according to Embodiment 3 of the present invention.
- FIG. 16 is an explanatory diagram showing an example of behavior of water of melted frost during defrosting in the corrugated fin heat exchanger including the corrugated fin 30 shown in FIG. 15 .
- FIG. 17 is a diagram showing a modification of the corrugated fin 30 in the corrugated fin heat exchanger according to Embodiment 3 of the present invention.
- FIG. 18 is an explanatory diagram showing an example of behavior of water of melted frost during defrosting in the corrugated fin heat exchanger including the corrugated fin 30 shown in FIG. 17 .
- FIG. 19 is a perspective view showing the configuration of a corrugated fin 30 in a corrugated fin heat exchanger according to Embodiment 4 of the present invention.
- FIG. 20 is a diagram showing a front view (a) and a side view (b) of the corrugated fin 30 in the corrugated fin heat exchanger according to Embodiment 4 of the present invention.
- FIG. 21 is an explanatory diagram showing an example of behavior of water of melted frost during defrosting in the corrugated fin heat exchanger according to Embodiment 4 of the present invention.
- FIG. 1 is a refrigerant circuit diagram showing a schematic configuration of the refrigeration cycle apparatus according to Embodiment 1.
- an air-conditioning apparatus is shown as an example of the refrigeration cycle apparatus.
- the relationship between the dimensions, the shapes, and the like of respective components may be different from actual relationship, shapes, and the like.
- the positional relationship e.g., the vertical relationship between respective components in the following description is that when the refrigeration cycle apparatus including the corrugated fin heat exchanger is installed in a usable state.
- the refrigeration cycle apparatus has a configuration in which a compressor 1 , a four-way valve 2 , a heat source side heat exchanger 3 , a pressure reducing device 4 , and a load side heat exchanger 5 are connected in a circuit via a refrigerant pipe.
- the refrigeration cycle apparatus includes an air-sending fan 6 that sends air to the heat source side heat exchanger 3 , and an air-sending fan 7 that sends air to the load side heat exchanger 5 .
- FIG. 1 shows only minimum necessary components as an air-conditioning apparatus that performs both cooling operation and heating operation.
- the refrigeration cycle apparatus may include, in addition to the components shown in FIG. 1 , pressure measuring means, a gas-liquid separator, a receiver, and an accumulator.
- the compressor 1 is a fluid machine that compresses low-pressure refrigerant sucked therein and discharges the refrigerant as high-pressure refrigerant.
- the four-way valve 2 serves to switch the flow direction of the refrigerant in a refrigeration cycle between during cooling operation and during heating operation.
- the heat source side heat exchanger 3 is a heat exchanger that serves as a radiator (e.g., a condenser) during cooling operation and serves as an evaporator during heating operation. In the heat source side heat exchanger 3 , heat is exchanged between the refrigerant flowing therein and air (outside air) sent by the air-sending fan 6 .
- the pressure reducing device 4 serves to reduce the pressure of the high-pressure refrigerant to make the refrigerant into low-pressure refrigerant.
- an electronic expansion valve capable of adjusting an opening degree or another valve is used.
- the load side heat exchanger 5 is a heat exchanger that serves as an evaporator during cooling operation and serves as a radiator (e.g., a condenser) during heating operation. In the load side heat exchanger 5 , heat is exchanged between the refrigerant flowing therein and air sent by the air-sending fan 7 .
- cooling operation refers to an operation in which the low-temperature and low-pressure refrigerant is supplied to the load side heat exchanger 5
- heating operation refers to an operation in which the high-temperature and high-pressure refrigerant is supplied to the load side heat exchanger 5 .
- frost occurs in the heat exchanger that serves as an evaporator, and the heat exchange efficiency of the heat exchanger may decrease. Therefore, when a condition for occurrence of frost is satisfied and cooling operation or heating operation is continued for a predetermined time period, defrosting operation is performed in which the flow direction of the refrigerant is switched by the four-way valve 2 and the high-temperature and high-pressure refrigerant (hot gas) is supplied to the evaporator. Whether the condition for occurrence of frost is satisfied is determined by a controller, which is not shown, on the basis of, for example, the dry-bulb temperature (e.g., 2 degrees C. or lower) and the relative humidity (e.g., 93.1% or higher) of the air at the evaporator side.
- the dry-bulb temperature e.g., 2 degrees C. or lower
- the relative humidity e.g., 93.1% or higher
- FIG. 2 is a perspective view showing the configuration of the corrugated fin heat exchanger according to Embodiment 1.
- the corrugated fin heat exchanger is used as at least one of the heat source side heat exchanger 3 and the load side heat exchanger 5 .
- the corrugated fin heat exchanger according to Embodiment 1 is of a vertical flow type in which internal fluid (the refrigerant in Embodiment 1) is caused to flow in the vertical direction.
- the corrugated fin heat exchanger has a configuration in which a plurality of flat tubes 10 aligned in parallel with each other and extending in the vertical direction (gravity direction) and at least one corrugated fin 30 disposed between the adjacent two flat tubes 10 are alternately stacked.
- each flat tube 10 The upper end of each flat tube 10 is connected to an upper header 12 , and the lower end of each flat tube 10 is connected to a lower header 13 .
- Each corrugated fin 30 has a configuration in which a metal plate is formed in a corrugated shape (wavy shape). In the corrugated fin heat exchanger, heat is exchanged between the refrigerant flowing in the vertical direction within the flat tubes 10 and sent air flowing in a direction crossing (e.g., orthogonal to) both the gravity direction and the stacking direction of the flat tubes 10 .
- FIG. 3 is a front view showing the configuration of the corrugated fin 30 in the corrugated fin heat exchanger according to Embodiment 1 as seen in the flow direction of the sent air.
- FIG. 3 shows adjacent two flat tubes 10 a and 10 b and one corrugated fin 30 disposed between the flat tubes 10 a and 10 b .
- the corrugated fin 30 includes: a plurality of top portions 31 that are in contact with the one flat tube 10 a , a plurality of top portions 32 that are in contact with the other flat tube 10 b , and a plurality of slant portions each provided between the top portion 31 and the top portion 32 and bridging between the flat tubes 10 a and 10 b .
- slant portions 33 a including slant portions 33 a 1 , 33 a 2 , . . .
- slant portions 33 b including slant portions 33 b 1 , 33 b 2 , . . .
- the flat tube 10 a and the top portions 31 , and the flat tube 10 b and the top portions 32 are joined by means of, for example, brazing.
- the multiple slant portions 33 a are not necessarily parallel with each other.
- the multiple slant portions 33 b are not necessarily parallel with each other. That is, the multiple slant portions 33 a and 33 b are inclined at a plurality of patterns of angles of inclination (e.g., angles of inclination ⁇ 1 to ⁇ 9 ) relative to a perpendicular line toward the flat tube 10 a .
- angles of inclination e.g., angles of inclination ⁇ 1 to ⁇ 9
- the multiple slant portions 33 a and 33 b include at least steep slant portions that are inclined at a relatively large angle of inclination (e.g., the angles of inclination ⁇ 2 , ⁇ 3 , ⁇ 6 , ⁇ 7 , ⁇ 8 , and ⁇ 9 ) relative to the perpendicular line toward the flat tube 10 a (e.g., the slant portions 33 a 1 , 33 b 2 , and 33 a 3 ) and gentle slant portions that are inclined at a relatively small angle of inclination (e.g., the angles of inclination ⁇ 1 , ⁇ 4 , and ⁇ 5 ) relative to the perpendicular line toward the flat tube 10 a (e.g., the slant portions 33 b 1 , 33 a 2 , 33 b 3 , 33 a 4 , 33 b 4 , and 33 a 5 ).
- a relatively large angle of inclination e.g., the angles of inclin
- the angles of inclination of the respective steep slant portions may be different form each other.
- the angles of inclination of the respective gentle slant portions may be different form each other.
- the angles of inclination of the steep slant portions are preferably greater than 10.05 degrees and more preferably 11.25 degrees or greater.
- the gentle slant portions are provided at a plurality of locations with at least one steep slant portion positioned therebetween. In the range shown in FIG. 3 , the gentle slant portions are provided at two locations with two steep slant portions (the slant portions 33 b 1 and 33 a 2 ) positioned therebetween.
- the steep slant portions are provided at a plurality of locations with at least one gentle slant portion positioned therebetween.
- the steep slant portions are provided at two locations with two gentle slant portions (the slant portions 33 b 2 and 33 a 3 ) positioned therebetween.
- Each of the multiple slant portions 33 a and 33 b is formed such that an end thereof on the lower end side of the corrugated fin 30 is positioned lower than the other end thereof on the upper end side of the corrugated fin 30 .
- the corrugated fin 30 has a configuration in which each of the slant portions is slanted monotonously downward from the upper end portion toward the lower end portion.
- the upper end portion of the corrugated fin 30 is the end portion at the upper header 12 side that is located at the upper side in the FIG. 2
- the lower end portion of the corrugated fin 30 is the end portion at the lower header 13 side that is located at the lower side in FIG. 2 .
- the plurality of top portions 31 (including top portions 31 - 1 , 31 - 2 , . . . ) and the plurality of top portions 32 (including top portions 32 - 1 , 32 - 2 , . . . ) respectively have a plurality of patterns of vertex angles.
- the vertex angle of each top portion 31 or 32 is defined as the sum of the angles of inclination of the slant portion 33 a and the slant portion 33 b located at both sides with the top portion 31 or 32 intervening therebetween.
- the top portions 31 and 32 include at least large vertex angle portions having a first vertex angle (e.g., the sum of relatively large angles of inclination) that is a relatively large angle (e.g., the top portions 31 - 1 , 31 - 3 , 32 - 4 , and 31 - 4 ), intermediate vertex angle portions having a second vertex angle (e.g., the sum of a relatively large angle of inclination and a relatively small angle of inclination) smaller than the first vertex angle (e.g., the top portions 32 - 1 , 32 - 2 , and 32 - 3 ), and small vertex angle portions having a third vertex angle (e.g., the sum of relatively small angles of inclination) smaller than the second vertex angle (e.g., the top portion 31 - 2 ).
- a first vertex angle e.g., the sum of relatively large angles of inclination
- intermediate vertex angle portions having a second vertex angle e.g., the sum of
- the large vertex angle portions are provided at a plurality of locations with one or more small vertex angle portions or intermediate vertex angle portions intervening therebetween, the intermediate vertex angle portions are provided at a plurality of locations with one or more small vertex angle portions or large vertex angle portions intervening therebetween, and the small vertex angle portions are provided at a plurality of locations with one or more intermediate vertex angle portions or large vertex angle portions intervening therebetween.
- FIG. 4 is a schematic diagram showing a production process for the corrugated fin 30 as a part of a production process for the corrugated fin heat exchanger according to Embodiment 1, and a production apparatus used in the process.
- the production apparatus used in the production process for the corrugated fin 30 includes a supply unit 50 , a shaping unit 60 , and a cutting unit 70 .
- the supply unit 50 includes a drum that holds a thin plate 51 made of metal (e.g., aluminum) wound in a roll shape.
- the supply unit 50 is configured to rotate the drum to supply the band-shaped thin plate 51 to the shaping unit 60 at the downstream side.
- the shaping unit 60 serves to shape the supplied thin plate 51 into a corrugated shape.
- the shaping unit 60 includes a pair of shaping rollers 61 and 62 .
- a plurality of teeth are provided along the axial directions thereof and mesh with each other with the thin plate 51 intervening therebetween.
- FIG. 5 is a diagram showing a schematic configuration in which the outer peripheral surfaces of the respective shaping rollers 61 and 62 are developed along a supply direction of the thin plate 51 (the right-left direction in the drawing).
- a plurality of teeth 61 a , 61 b , and 61 c having shapes (e.g., vertex angles) different from each other are provided on the outer peripheral surface of the shaping roller 61 so as to project radially outward.
- a vertex angle of the tooth 61 a is ⁇ 1 a
- a vertex angle of the tooth 61 b is ⁇ 1 b
- a vertex angle of the tooth 61 c is ⁇ 1 c .
- a plurality of teeth 62 a , 62 b , 62 c , and 62 d that mesh with the teeth 61 a , 61 b , and 61 c and have shapes (e.g., vertex angles) different form each other are provided on the outer peripheral surface of the shaping roller 62 so as to project radially outward.
- a vertex angle of the tooth 62 a is ⁇ 2 a
- a vertex angle of the tooth 62 b is ⁇ 2 b
- a vertex angle of the tooth 62 c is ⁇ 2 c
- a vertex angle of the tooth 62 d is ⁇ 2 d .
- the vertex angles ⁇ 1 a and ⁇ 1 c correspond to the above first vertex angle, which is the relatively large angle.
- the vertex angles ⁇ 2 a , ⁇ 2 b , ⁇ 2 c , and ⁇ 2 d correspond to the above second vertex angle, which is smaller than the first vertex angle.
- the vertex angle ⁇ 1 b corresponds to the above third vertex angle, which is smaller than the second vertex angle.
- the cutting unit 70 serves to cut the thin plate 51 shaped into the corrugated shape by the shaping unit 60 , in a predetermined length to produce the corrugated fin 30 .
- the band-shaped thin plate 51 supplied from the supply unit 50 is shaped by the shaping rollers 61 and 62 , and the shaped thin plate 51 is cut in a predetermined length by the cutting unit 70 . Accordingly, the corrugated fin 30 having a plurality of top portions 31 and 32 having vertex angles different from each other.
- a plurality of the corrugated fins 30 produced and a plurality of flat tubes 10 produced in another process are alternately stacked, and a pair of side plates and the like are disposed at both end sides in the stacking direction. Then, the upper header 12 and the lower header 13 are connected to one end and another end of each flat tube 10 , respectively. Accordingly, an assembly of the corrugated fin heat exchanger is produced.
- the produced assembly is heated to a temperature equal to or higher than the melting point of a brazing material, whereby the components of the assembly are brazed to each other, so that the corrugated fin heat exchanger is produced.
- FIG. 6 is a front view showing the configuration of a part of a corrugated fin heat exchanger used in the actual machine test.
- Dp the distance between the central axis of the flat tube 10 a and the central axis of the flat tube 10 b is denoted by Dp [mm]
- Dp the distance between the central axis of the flat tube 10 a and the central axis of the flat tube 10 b is denoted by Dp [mm]
- Fp [mm] the distance (fin pitch) from the middle position between the top portion 31 and the top portion 32 of the corrugated fin 30 to the next middle position is denoted by Fp [mm]
- ⁇ [degrees] the vertex angle of the top portion 31 or 32 of the corrugated fin 30
- the flow direction of the internal fluid is set to be the gravity direction
- the range of the vertex angle ⁇ is set as 0 degrees ⁇ 180 degrees, and the range of the angle of inclination ⁇ is set as 0 degrees ⁇ 90 degrees.
- each parameter described above including the fin pitch Fp, the vertex angle ⁇ , and the angle of inclination ⁇ is substantially uniform over the entirety of the heat exchanger.
- FIG. 7 is a diagram showing the results of the actual machine test.
- frost 35 adhered over the entirety of the corrugated fin 30 .
- hot gas was passed through the flat tubes 10 a and 10 b to start defrosting.
- the fin efficiency is low since the distance from the flat tubes 10 a and 10 b thereto is large. Therefore, as shown in FIG.
- frost 35 adhered over the entirety of the corrugated fin 30 .
- hot gas was passed through the flat tubes 10 a and 10 b to start defrosting.
- the sherbet-like frost 35 remained on the center portion of each slant portion 33 a or 33 b of the corrugated fin 30 .
- the angle of inclination ⁇ is preferably greater than 10.05 degrees (e.g., the vertex angle ⁇ is greater than 20.1 degrees), and the angle of inclination ⁇ is more preferably 11.25 degrees or greater (e.g., the vertex angle ⁇ is 22.5 degrees or greater).
- each slant portion 33 a or 33 b that is the steep slant portion is preferably, for example, approximately 11.25 degrees.
- FIG. 10 is a boundary diagram showing a boundary between presence and absence of sliding-down of the frost 35 in the relationship between the distance Dp between the adjacent flat tubes 10 and the fin pitch Fp.
- the horizontal axis represents the distance Dp
- the vertical axis represents the fin pitch Fp.
- the region in which the distance Dp and the fin pitch Fp do not satisfy the relationship of the expression (1) is shown as an “unsliding-down region”. That is, when the relationship between the distance Dp and the fin pitch Fp is included in the unsliding-down region, it is not possible to sufficiently slide down the frost 35 during defrosting.
- each slant portion 33 a , 33 b In addition, to make the angle of inclination ⁇ of each slant portion 33 a , 33 b equal to or greater than 11.25 degrees, the distance Dp and the fin pitch Fp need to satisfy the relationship of the following expression (2). Fp ⁇ 0.1989 ⁇ Dp ⁇ 0.2983 (2)
- the region in which the distance Dp and the fin pitch Fp satisfy the relationship of the expression (2) is shown as a “sliding-down region”. That is, when the relationship between the distance Dp and the fin pitch Fp is included in the sliding-down region, it is possible to sufficiently slide down the frost 35 during defrosting.
- FIG. 11 is an explanatory diagram showing an example of behavior of frost in the corrugated fin heat exchanger, and a diagram showing (a) a state in the first half of defrosting and (b) a state in a later period of defrosting thereof.
- FIG. 11 (a) and (b) are front views corresponding to those of FIG. 3 .
- the condition for occurrence of frost e.g., the dry-bulb temperature of air at the evaporator side is 2 degrees C. or lower and the relative humidity is 93.1% or higher
- the four-way valve 2 is switched for defrosting, and high-temperature refrigerant (hot gas) flows through the flat tubes 10 of the corrugated fin heat exchanger.
- frost 35 remains on the center portion of each slant portion 33 a or 33 b at which the fin efficiency is low.
- the frost 35 on the slant portions 33 b 1 , 33 a 2 , 33 b 3 , 33 a 4 , and 33 b 4 (steep slant portions) inclined at a relatively large angle of inclination ⁇ (e.g., ⁇ >10.05 degrees) slides down to the vicinity of the flat tube 10 a or the flat tube 10 b .
- ⁇ e.g., ⁇ >10.05 degrees
- the frost 35 on the slant portions 33 b 2 and 33 a 3 (gentle slant portions) inclined at a relatively small angle of inclination ⁇ (e.g., ⁇ 10.05 degrees) almost does not slide down to the vicinity of the flat tube 10 a or the flat tube 10 b .
- the frost 35 is melted on the center portions of the slant portions 33 b 2 and 33 a 3 .
- the distance between the top portion 31 and the top portion 32 is shorter than that at the steep slant portions, and thus the fin efficiency is high. Therefore, even when the frost 35 is melted on the center portions of the slant portions 33 b 2 and 33 a 3 , it is possible to further shorten the time period required for defrosting.
- all the slant portions 33 a and 33 b of the corrugated fin 30 are gentle slant portions inclined at a relatively small angle of inclination ⁇ (e.g., ⁇ 10.05 degrees).
- ⁇ e.g., ⁇ 10.05 degrees
- sliding-down of the frost 35 does not occur on all the slant portions 33 a and 33 b , and thus the time period required for defrosting becomes relatively long.
- the fin pitch Fp becomes small and the heat transfer area becomes large, and thus the heat exchange efficiency becomes high.
- Embodiment 1 When gentle slant portions and steep slant portions are present together as in Embodiment 1, it is effective to partially densely dispose the gentle slant portions having a smaller angle of inclination in order to make sliding-down of frost occur on more slant portions and decrease the average fin pitch.
- the number of the steep slant portions of the corrugated fin 30 is smaller than the number of the gentle slant portions.
- the corrugated fin heat exchanger according to Embodiment 1 includes the flat tubes 10 a and 10 b aligned in parallel with each other, and the corrugated fin 30 disposed between the flat tube 10 a and the flat tube 10 b , and the corrugated fin 30 includes: the slant portion 33 a 1 (an example of a first slant portion) and the slant portion 33 b 2 (an example of a second slant portion) that bridge between the flat tube 10 a and the flat tube 10 b and are inclined at an angle of inclination ⁇ 1 (an example of a first angle of inclination) and an angle of inclination ⁇ 4 (an example of a second angle of inclination) relative to the perpendicular line toward the flat tube 10 a , respectively; and the slant portion 33 b 1 and the slant portion 33 a 2 (an example of a third slant portion) that bridge between the flat tube 10 a and the flat tube 10 b , are disposed between the
- the fin efficiency is higher than that at the slant portions 33 b 1 and 33 a 2 , and thus it is possible to melt the frost 35 in a relatively short time period.
- gentle slant portions on which water of melted frost during defrosting is hard to be drained are provided at a plurality of locations with steep slant portions positioned therebetween. Accordingly, it is possible to disperse the gentle slant portions without making the gentle slant portions dense, and thus it is possible to prevent water of melted frost from being held concentrated in a specific portion of the heat exchanger at end of defrosting. Therefore, even when water expands during re-frosting, it is possible to prevent the heat exchanger from being broken. Thus, it is possible to increase the life of the corrugated fin heat exchanger.
- each of the angles of inclination ⁇ 1 and ⁇ 4 is 10.05 degrees or less, and each of the angles of inclination ⁇ 2 and ⁇ 3 is greater than 10.05 degrees. Accordingly, during defrosting, it is possible to slide down the frost 35 on the steep slant portions to the flat tubes 10 . Moreover, it is possible to decrease the average fin pitch Fp, and it is possible to inhibit the heat transfer area of the corrugated fin 30 from decreasing.
- each of the angles of inclination ⁇ 2 and ⁇ 3 may be 11.25 degrees or greater. Accordingly, during defrosting, it is possible to more assuredly slide down the frost 35 on the steep slant portions to the flat tubes 10 .
- the corrugated fin 30 has a plurality of slant portions including the slant portions 33 a 1 , 33 b 1 , 33 a 2 , and 33 b 2 , and the number of the slant portions inclined at an angle of inclination greater than 10.05 degrees relative to the perpendicular line toward the flat tube 10 a , of the plurality of slant portions, may be smaller than the number of the slant portions inclined at an angle of inclination 10.05 degrees or less relative to the perpendicular line toward the flat tube 10 a . Accordingly, it is possible to cause sliding-down of frost on more slant portions while keeping the average fin pitch Fp small.
- each of the plurality of slant portions 33 a and 33 b is formed such that an end thereof on the lower end side of the corrugated fin 30 is positioned lower than the other end thereof on the upper end side of the corrugated fin 30 .
- the production apparatus for the corrugated fin according to Embodiment 1 includes: the supply unit 50 that supplies the band-shaped thin plate 51 ; the shaping unit 60 that shapes the thin plate 51 supplied from the supply unit 50 , into a corrugated shape; and the cutting unit 70 that cuts the thin plate 51 shaped by the shaping unit 60 to produce the corrugated fin 30 .
- the shaping unit 60 includes the pair of shaping rollers 61 and 62 that mesh with each other with the thin plate 51 intervening therebetween.
- the plurality of teeth 61 a to 61 c and 62 a to 62 d having shapes different from each other are formed on the outer peripheral surfaces of the pair of shaping rollers 61 and 62 .
- the method for producing the corrugated fin heat exchanger according to Embodiment 1 includes a step of producing the corrugated fin 30 by using the production apparatus for the corrugated fin.
- FIG. 12 is a front view showing the configuration of a corrugated fin 30 in the corrugated fin heat exchanger according to Embodiment 2.
- Components having the same functions and operations as in Embodiment 1 are designated by the same reference signs, and the description thereof is omitted.
- the corrugated fin 30 of Embodiment 2 has a louver 100 formed at each slant portion 33 a or 33 b .
- the louver 100 of Embodiment 2 is provided to each slant portion 33 a or 33 b and at the center portion between the flat tubes 10 a and 10 b .
- the louver 100 is, for example, a cut/raised-type louver formed by cutting and raising the slant portion 33 a or 33 b .
- the position of the louver 100 is not limited to the center portion between the flat tubes 10 a and 10 b , and the louver 100 may be provided so as to be closer to one of the flat tubes 10 a and 10 b .
- the louver 100 may be provided over the entire surface of each slant portion 33 a or 33 b other than the vicinities of the top portions 31 and 32 .
- FIG. 13 is an explanatory diagram showing an example of behavior of water of melted frost during defrosting in the corrugated fin heat exchanger.
- FIG. 13 an example of flow of the water of melted frost is shown by arrows.
- the louver 100 is formed at each of the plurality of slant portions 33 a and 33 b . According to this configuration, it is possible to improve the transferring performance of the heat exchanger by the front edge effect of the louver 100 .
- Embodiment 2 it is possible to drain water of melted frost generated during defrosting, in the gravity direction via the louver 100 . Accordingly, the number of drainage paths for water of melted frost increases, and thus it is possible to shorten the time period required for water drainage.
- Embodiment 2 since it is possible to allow water of melted frost from above to flow into the vertex angle side (inner side) of the top portions 31 and 32 of the corrugated fin 30 , it is possible to drain downward water of melted frost that exceeds a water-holding allowable limit at the top portions 31 and 32 . Moreover, by discharging water of melted frost accumulated at the top portions 31 and 32 , it is possible to decrease the amount of water held in the entirety of the corrugated fin heat exchanger. Therefore, it is possible to prevent the heat exchanger from being broken due to expansion of water during re-frosting.
- FIG. 14 is a perspective view showing the configuration of a corrugated fin 30 in the corrugated fin heat exchanger according to Embodiment 3.
- Components having the same functions and operations as in Embodiment 1 are designated by the same reference signs, and the description thereof is omitted.
- the corrugated fin 30 of Embodiment 3 has a plurality of slits 101 (through holes) formed so as to penetrate between one surface and the other surface.
- the slits 101 are provided to portions that are in contact with the flat tube 10 (the top portions 31 , 32 ), or in the vicinities thereof.
- FIG. 15 is a diagram showing a front view (a) and a side view (b) of the corrugated fin 30 .
- the leftward direction in FIG. 15 represents the gravity direction.
- an example of flow of water of melted frost is indicated by arrows.
- the slits 101 of this example have a semi-elliptical shape and are provided to a portion above each top portion 31 or 32 (e.g., above the centers of the top portions 31 and 32 .
- FIG. 16 is an explanatory diagram showing an example of behavior of water of melted frost during defrosting in the corrugated fin heat exchanger including the corrugated fin 30 shown in FIG. 15 .
- FIG. 16 an example of flow of water of melted frost is shown by arrows.
- water of melted frost is drained downward on the corrugated fin 30 while flowing down from the upper surface of the corrugated fin 30 to the lower surface via the slits 101 .
- FIG. 17 is a diagram showing a modification of the corrugated fin 30 .
- the leftward direction in FIG. 17 represents the gravity direction.
- an example of flow of water of melted frost is indicated by arrows.
- the slits 101 of this modification have an elliptical shape and are provided to upper portions and lower portions of the top portions 31 and 32 .
- FIG. 18 is an explanatory diagram showing an example of behavior of water of melted frost during defrosting in the corrugated fin heat exchanger including the corrugated fin 30 shown in FIG. 17 .
- FIG. 18 an example of flow of water of melted frost is shown by arrows.
- water of melted frost flows downward on the corrugated fin 30 , and also flows in the gravity direction on the flat tubes 10 through the slits 101 . Therefore, according to the configuration of this modification, it is possible to drain the water of melted frost on the corrugated fin 30 , and it is also possible to drain the water of melted frost in the gravity direction on the flat tubes 10 .
- the slits 101 are formed in the corrugated fin 30 .
- the slits 101 are provided to the top portions 31 and 32 in the corrugated fin heat exchanger according to Embodiment 3.
- FIG. 19 is a perspective view showing the configuration of a corrugated fin 30 in the corrugated fin heat exchanger according to Embodiment 4.
- Components having the same functions and operations as in Embodiment 1 are designated by the same reference signs, and the description thereof is omitted.
- a plurality of slits 101 are formed in the corrugated fin 30 of Embodiment 4 so as to penetrate between one surface and the other surface.
- the slits 101 are provided to slant portions 33 a and 33 b (e.g., above top portions 31 and 32 of the slant portions 33 a and 33 b ).
- Contact surfaces of the corrugated fin 30 with each flat tube 10 are formed over the entirety in the width direction of the corrugated fin 30 .
- FIG. 20 is a diagram showing a front view (a) and a side view (b) of the corrugated fin 30 .
- the leftward direction in FIG. 20 represents the gravity direction.
- an example of flow of water of melted frost is indicated by arrows.
- the slits 101 are provided, for example, below the center portion of each slant portion 33 a or 33 b.
- FIG. 21 is an explanatory diagram showing an example of behavior of water of melted frost during defrosting in the corrugated fin heat exchanger according to Embodiment 4.
- FIG. 21 an example of flow of the water of melted frost is indicated by arrows.
- the water of melted frost flows downward on the corrugated fin 30 through the slits 101 .
- the slits 101 are formed in the corrugated fin 30 .
- the slits 101 are provided to a plurality of the slant portions 33 a and 33 b.
- Embodiment 4 since the slits 101 are provided to the slant portions 33 a and 33 b , it is possible to prevent the area of contact between the corrugated fin 30 and each flat tube 10 from decreasing, as compared to the configuration of Embodiment 3. Therefore, it is possible to efficiently transmit heat during defrosting from each flat tube 10 to the corrugated fin 30 , and it is also possible to immediately drain water of melted frost.
- the present invention is not limited to Embodiments 1 to 4 described above, and various modifications may be made.
- the air-conditioning apparatus has been taken as an example of the refrigeration cycle apparatus, but the present invention is also applicable to refrigeration cycle apparatuses other than the air-conditioning apparatus.
Abstract
Description
θ=2×tan−1((Fp/2)/(H/2))
Fp>0.1776×Dp−0.2666 (1)
Fp≥0.1989×Dp−0.2983 (2)
Claims (14)
Applications Claiming Priority (1)
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PCT/JP2015/063671 WO2016181509A1 (en) | 2015-05-12 | 2015-05-12 | Corrugated fin-type heat exchanger, refrigeration cycle device, device for producing corrugated fins, and method for producing corrugated fin-type heat exchanger |
Publications (2)
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US20180058780A1 US20180058780A1 (en) | 2018-03-01 |
US10488124B2 true US10488124B2 (en) | 2019-11-26 |
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US15/558,582 Active US10488124B2 (en) | 2015-05-12 | 2015-05-12 | Corrugated fin heat exchanger, refrigeration cycle apparatus, apparatus for producing corrugated fin, and method for producing corrugated fin heat exchanger |
Country Status (4)
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US (1) | US10488124B2 (en) |
JP (1) | JP6685292B2 (en) |
CN (1) | CN107532864A (en) |
WO (1) | WO2016181509A1 (en) |
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JP6911549B2 (en) * | 2017-06-12 | 2021-07-28 | 株式会社デンソー | Heat exchanger and corrugated fins |
CN110741218B (en) | 2017-06-12 | 2021-11-19 | 株式会社电装 | Heat exchanger and corrugated fin |
US11161621B2 (en) * | 2018-01-18 | 2021-11-02 | Raytheon Technologies Corporation | Heat exchanger with moving ice filter |
DE102020100105A1 (en) * | 2020-01-06 | 2021-07-08 | Volkswagen Aktiengesellschaft | Heat exchanger |
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JP2004150710A (en) * | 2002-10-30 | 2004-05-27 | Denso Corp | Refrigerant evaporator and its manufacturing method |
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2015
- 2015-05-12 JP JP2017517526A patent/JP6685292B2/en active Active
- 2015-05-12 US US15/558,582 patent/US10488124B2/en active Active
- 2015-05-12 CN CN201580079561.8A patent/CN107532864A/en active Pending
- 2015-05-12 WO PCT/JP2015/063671 patent/WO2016181509A1/en active Application Filing
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Also Published As
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JP6685292B2 (en) | 2020-04-22 |
JPWO2016181509A1 (en) | 2017-11-30 |
US20180058780A1 (en) | 2018-03-01 |
CN107532864A (en) | 2018-01-02 |
WO2016181509A1 (en) | 2016-11-17 |
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